KR20120062718A - Multi-ratio transmission - Google Patents

Abstract

The present invention relates to a multi-stage transmission including a nine-speed forward gear and one reverse gear, wherein the multi-speed transmission includes four planetary gear sets (P1, P2, P3, and P4) and eight rotatable shafts (1). , 2, 3, 4, 5, 6, 7, 8, 8 ') and six shifting members O3, O4, 13, 16, 18, 48, 67, and planetary gear set P1 The sun gear is operatively connected with the input shaft 1, the input shaft 1 is connected to the third shaft 3 via the first clutch 13 and the sixth shaft via the second clutch 16. 6), and the third shaft 3 is connected to the carrier of the planetary gear set P2 and the ring gear of the planetary gear set P3 and through the first brake O3 to the housing G. And the fourth shaft 4 can be coupled to the housing G of the transmission via the second brake O4 and connected to the ring gear of the planetary gear set P2 and to the planetary gear set P1. Works with the carrier The sixth shaft 6 is connected to the sun gear of the planetary gear set P4 and is connected to the seventh shaft 7 via the third clutch 67, and the seventh shaft is the planetary gear set P3. Is connected to the sun gear of the planetary gear set P2 and the ring gear of the planetary gear set P1 is rotatably connected to the housing G, and the fifth shaft 5 is the planetary gear set ( The carrier of P3 and the ring gear of the planetary gear set P4 are connected, and the output shaft 2 is connected with the carrier of the planetary gear set P4.

Description

Multi-stage transmission {MULTI-RATIO TRANSMISSION}

The present invention relates to a multi-speed transmission of the planetary gear structure, in particular an automatic transmission for automobiles, according to the preamble of claim 1.

In particular, automatic transmissions for automobiles comprise planetary gear sets according to the prior art, which planetary gear sets are shifted by friction or shifting members such as, for example, clutches and brakes, and are typically used, for example, as hydrodynamic torque converters or fluid clutches. Under the influence of the slip action, it is optionally connected with a starting member with a lockup clutch.

Automatic transmissions of this type are known, for example, from DE 199 49 507 A1 of the applicant. In the German publication, the input shaft is provided with two front-mounted gear sets that cannot be shifted, these front-mounted gear sets produce two rotational speeds on the output side, and these rotational speeds In addition to the rotational speed of the input shaft, is selected as long as only one shifting member is connected or disconnected from each of the two shifting members that are directly operated for switching from one shifting stage to the next higher or lower shifting stage, respectively. In such a way, it can be shifted into a double planetary gear set that can be shifted while acting on the output shaft by selective engagement of the shifting members used.

In this case, seven forward shift stages are achieved under the condition that five shifting members are used, and nine forward or ten forward shift stages are achieved under the condition that six shifting members are used.

Also, from DE 102 13 820 A1 a multistage automatic transmission is known which comprises eight forward shift stages and one reverse shift stage, which comprises a first input path T1 of a first transmission ratio, An input path T2 having a transmission ratio larger than the input path T1, and a Rabinoux type planetary gear set including four members, the four members being the first in the order of the members in the speed diagram. The planetary gear set, which is a member, a second member, a third member, and a fourth member, a clutch C-2 for transmitting rotation of the input path T2 to the first member S3, and an input path T2. The clutch C-1 for transmitting the rotation of the input path to the fourth member S2, the clutch C-4 for transmitting the rotation of the input path T1 to the first member, and the rotation of the input path T1. Engagement of the clutch C-3, which is transmitted to the second member C3, the brake B-1 that forms the engagement of the fourth member, and the engagement of the second member, And a castle output member connected with the brake (B-2), and a third member (S3) to.

A nine-speed multistage transmission is also known from DE 29 36 969 A1. The nine-speed multi-speed transmission includes eight shifting members and four gear sets, one gear set is used as a front mounted gear unit and the main gear unit is a Simpson gear set and a reverse gear unit. Includes additional gear sets used.

Further multistage transmissions are known, for example, from DE 10 2005 010 210 A1 and DE 10 2006 006 637 A1.

In general, a vehicle transmission with a planetary gear structure capable of automatic shifting has already been described many times in the prior art and is constantly being further developed and improved. The transmission therefore requires low construction costs, in particular a small number of shifting members, and in a sequential shifting scheme it is necessary to avoid double shifting, so that each shift in the specified gear shift range Only one shifting member is changed.

Applicant DE 102008000428.3, which has not yet been disclosed, is known from a planetary gear structure multistage transmission comprising an input and an output disposed inside the housing. In the case of known transmissions, at least four planetary gear sets, referred to below as first, second, third and fourth planetary gear sets, and input shafts, output shafts, third, fourth, fifth, Six or more shifting members are provided, including brakes and clutches, as well as eight or more rotatable shafts, referred to as sixth, seventh and eighth shafts, the selective engagement of these shifting members with an input and an output. Various speed ratios are generated between the parts, whereby preferably, nine forward shift stages and one reverse shift stage can be realized.

The first and second planetary gear sets, preferably here formed as negative planetary gear sets, form a shiftable front mounted gear set, and the third and fourth planetary gear sets form a main gear set.

In the case of a known multistage transmission, the carriers of the first and second planetary gear sets are connected to each other via a fourth shaft which is connected with the member of the main gear set, and the ring gear of the first planetary gear set is connected via the first clutch. Connected to the sun gear of the second planetary gear set via an eighth shaft that can be detachably connected to the input shaft, the sun gear of the first planetary gear set being coupled to the housing of the transmission via a first brake by a third shaft. And a removably connected to the input shaft via the second clutch, and the ring gear of the second planetary gear set can be coupled to the housing of the transmission via the second brake by the fifth shaft. In addition, the seventh shaft can be continuously connected with one or more members of the main gear set and can be coupled to the housing of the transmission via a third brake, and the sixth shaft is continuously connected with one or more additional members of the main gear set and The third clutch may be detachably connected to the input shaft. The output shaft is continuously connected with one or more additional members of the main gear set.

Preferably, in the case of known transmissions, the fourth shaft is continuously connected with the ring gear of the third planetary gear set, and the sixth shaft is continuously connected with the ring gear of the fourth planetary gear set and the carrier of the third planetary gear set. And may be detachably connected to the input shaft through the third clutch. The seventh shaft can also be continuously connected to the sun gears of the third and fourth planetary gear sets and coupled to the housing of the transmission via the third brake. The output here is via an output shaft which is in continuous connection with the carrier of the fourth planetary gear set. In addition, the third and fourth planetary gear sets may be configured or reduced with a Lavigno gear set that includes a cavity carrier and a cavity ring gear.

The object of the present invention is to achieve an optimal construction cost and mounting size, in particular mounting length and weight, in the first mentioned type of multistage transmission comprising nine forward and one or more reverse shifting stages with sufficient transmission ratios. Another object of the present invention is to propose the multi-stage transmission in which efficiency is also improved in relation to drag loss and tooth friction loss. A further object of the present invention is to allow a small support moment to act on the shifting members in the multistage transmission according to the invention. In particular, an object of the present invention is to configure the transmission according to the present invention to be suitable for the front wheel rolling lateral structure.

This object is achieved according to the invention by the features of claim 1. Further advantages and preferred embodiments are presented from the dependent claims.

Accordingly, a multistage transmission according to the present invention of the planetary gear structure including an input part and an output part disposed in the housing is proposed. Four or more planetary gear sets, also referred to below as first, second, third and fourth planetary gear sets, and input shafts, output shafts, third, fourth, fifth, sixth, In addition to eight rotatable shafts, referred to as seventh and eighth shafts, six or more shifting members are provided, including brakes and clutches, with the optional engagement of these shifting members varying between the input and output sections. In this way, preferably, nine forward shift stages and one reverse shift stage can be realized.

The planetary gear sets are arranged in the order of the first planetary gear set, the second planetary gear set, the third planetary gear set, the fourth planetary gear set in the axial direction and are preferably formed as a negative planetary gear set.

A simple negative planetary gear set includes, as is known, a sun gear, a ring gear and a carrier, the carrier being rotatably mounted with planetary gears meshing with the sun gear and the ring gear, respectively. The ring gear thereby takes the opposite direction of rotation with respect to the sun gear when the carrier is fixed. In contrast, a simple plus planetary gear set includes a sun gear, a ring gear and a carrier, the carrier being rotatably mounted with internal and external planetary gears, all internal planetary gears meshing with the sun gear and all external planetary gears Meshes with a ring gear, each inner planet gear meshes with a respective outer planet gear. The ring gear thereby takes the same direction of rotation as the sun gear when the carrier is fixed.

According to the invention the sun gear of the first planetary gear set is operatively connected with the input shaft, the input shaft can be detachably connected with the third shaft via the first clutch and with the sixth shaft via the second clutch The third shaft is connected to the carrier of the second planetary gear set and the ring gear of the third planetary gear set and is coupled to the housing of the transmission via the first brake, and the fourth shaft is connected to the housing of the transmission via the second brake. It can be connected to the housing and is connected to the ring gear of the second planetary gear set and is operatively connected to the carrier of the first planetary gear set, the sixth shaft is connected to the sun gear of the fourth planetary gear set and the seventh through the third clutch The seventh shaft is connected to the sun gear of the third planetary gear set and the sun gear of the second planetary gear set.

In addition, the ring gear of the first planetary gear set is rotatably connected with the housing of the transmission, the fifth shaft is connected with the carrier of the third planetary gear set and the ring gear of the fourth planetary gear set, and the output shaft is fourth It is connected with the carrier of the planetary gear set.

Preferably, the sun gear of the first planetary gear set is directly connected with the input shaft, and the carrier of the first planetary gear set has an eighth shaft, a fourth shaft, and an eighth shaft connected with the carrier of the first planetary gear set. A fourth clutch that is detachably connected to each other, and a fourth shaft that is connected to the ring gear of the second planetary gear set, may be detachably connected to the ring gear of the second planetary gear set.

According to a variant of the invention, the input shaft is not directly but through an additional shaft connected with the sun gear of the first planetary gear set and with an additional clutch removably connecting the additional shaft and the input shaft. It can be detachably connected to the gear, in which case the carrier of the first planetary gear set is directly connected with the ring gear of the second planetary gear set via the fourth shaft.

An embodiment according to the invention of a multistage transmission provides an increased total ratio spread of the multistage transmission and in particular a transmission ratio suitable for a passenger car, whereby an improvement in driving comfort and significant fuel economy reduction are achieved.

In addition, the use of a multi-stage transmission according to the present invention greatly reduces the construction cost through a small number of shifting members. Preferably, the multi-stage transmission according to the invention makes it possible to carry out starting with a hydrodynamic converter, an external starting clutch or other suitable external starting members. It is also conceivable to enable the starting process using a starting member integrated inside the transmission. Preferably shifting members operated in the first forward gear stage and the reverse gear stage are suitable.

In addition, in the case of a multistage transmission according to the present invention, excellent efficiency is provided in main driving gears with respect to drag loss and tooth friction loss.

In addition, there is a small moment in the planetary gear sets and the shifting members of the multistage transmission, whereby wear in the multistage transmission is preferably reduced. In addition, with a small moment, correspondingly small dimensions are possible, thereby reducing the required mounting space and corresponding costs. In addition there is a low rotational speed in the shafts, the shifting members and the planetary gear sets.

In addition, the transmission according to the present invention can be customized to be suitable for various power transmission device configurations not only in the direction of power flow but also in space.

The invention is explained in more detail by way of example in accordance with the accompanying drawings in the following.
1 is a schematic view showing a first preferred embodiment of a multistage transmission according to the present invention.
Figure 2 is a schematic diagram showing a second preferred embodiment of a multistage transmission according to the present invention.
3 is an exemplary shifting pattern for the multi-stage transmission according to FIG. 1.

1 shows a multistage transmission according to the invention comprising an input shaft 1 arranged inside a housing G, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4. It is. Planetary gear sets P1, P2, P3 and P4 are formed as negative planetary gear sets for the embodiment shown in FIG. According to the invention, if at the same time the carrier and ring gear connections are exchanged and the value of the standard transmission ratio is increased by one, one or more planetary gear sets can be formed as a positive planetary gear set.

In the illustrated embodiment, the planetary gear sets are arranged in the order of P1, P2, P3, P4 when viewed in the axial direction.

As can be seen from FIG. 1, six shifting members are provided, namely two brakes O3, O4 and four clutches 13, 16, 48 and 67. The spatial arrangement of the shifting members can be made arbitrarily and limited only by the dimensions and the external shape. The clutches and brakes of the transmission are preferably formed as friction shifting members or multi-plate shifting members.

By the shifting members, selective shifting of nine forward shift stages and one reverse shift stage can be realized. The multistage transmission of the invention according to FIG. 1 comprises a total of eight rotatable shafts, namely shafts 1, 2, 3, 4, 5, 6, 7 and 8, the input shaft being the first shaft of the transmission. And the output shaft forms the second shaft of the transmission.

In the embodiment shown in FIG. 1, the sun gear of the first planetary gear set P1 is directly connected with the input shaft 1, the input shaft is connected with the third shaft 3 via the first clutch 13, and The second clutch 16 may be detachably connected to the sixth shaft 6. Here, the third shaft 3 is connected to the carrier of the second planetary gear set P2 and the ring gear of the third planetary gear set P3 and is coupled to the housing G of the transmission via the first brake O3. Can be. In addition, the sixth shaft 6 may be connected to the sun gear of the fourth planetary gear set P4 and may be detachably connected to the seventh shaft 7 through the third clutch 67. ) Is connected to the sun gear of the third planetary gear set P3 and the sun gear of the second planetary gear set P2.

As can be seen in FIG. 1, the carrier of the first planetary gear set P1 can be detachably connected to the fourth shaft 4 via the eighth shaft 8 and the fourth clutch 48, and the fourth shaft May be connected to the ring gear of the second planetary gear set P2 and coupled to the housing G of the transmission via the second brake O4. In addition, the ring gear of the first planetary gear set P1 is rotatably connected to the housing G of the transmission by the shaft O, and the fifth shaft 5 is a carrier of the third planetary gear set P3. And a ring gear of the fourth planetary gear set P4, and the output shaft 2 is connected to a carrier of the fourth planetary gear set P4.

According to the invention the second clutch 16 and the third clutch 67 can be arranged between the third planetary gear set P3 and the fourth planetary gear set P4 when viewed in the axial direction and have a common outer disk. The carrier may include a carrier, and the first clutch 13 and the fourth clutch 48 may be disposed between the first planetary gear set P1 and the second planetary gear set P2 when viewed in the axial direction.

Further, the first brake O3 and the second brake O4 are preferably arranged side by side with each other in the axial direction.

In the scope of the further embodiment of the invention, which is the subject of FIG. 2, an eighth shaft 8 connected with a carrier of the first planetary gear set P1 and a ring gear of the second planetary gear set P2 are connected. Of the ring gear and the first planetary gear set P1 of the second planetary gear set P2 formed through a fourth clutch 48 that detachably connects the fourth shaft 4 and the eighth shaft 8 to each other. The detachable connection of the carrier can be replaced by a direct connection by the fourth shaft 4, in which case the direct connection of the sun gear of the first planetary gear set P1 and the input shaft 1 is the first planetary gear set. It is replaced by a detachable connection by means of an additional clutch 18 which detachably connects the input shaft 1 with an additional shaft 8 'which is connected to the sun gear of P1.

3 shows an exemplary shifting pattern of the multistage transmission according to FIG. 1. Three shifting members are fastened to each shift stage. From the shifting pattern, the shift ratio (i) of each of the individual shift stages and the adjacent shift ratio difference or adjacent gear ratio difference (phi) determined from the respective shift ratios for higher subsequent shift stages can be seen as an example, with a value of 8.993. Represents the spread of the transmission.

The standard values for the standard transmission ratios of the planetary gear sets P1, P2, P3 and P4 formed as negative planetary gear sets are -1.80, -3.554, -1.851 and -2.265, respectively. As can be seen from FIG. 3, in the sequential shifting scheme, double shifting or group shifting is prevented because two adjacent shifting stages jointly use two shifting members. Also, as can be seen, a large spread is achieved in a condition where the adjacent speed ratio difference is small.

The first forward shift stage is provided by engagement of the first brake O3 and the second and fourth clutches 16, 48, and the second forward shift stage is formed of the first and second brakes O3 and O4. 2 is provided by the engagement of the clutch 16, the third forward speed is provided by the engagement of the first brake (O3) and the second and third clutch (16, 67), the fourth forward speed is 2 brake O4 and the second and third clutches 16 and 67, and the fifth forward shift stage is provided by the engagement of the second, third and fourth clutches 16, 67 and 48, The sixth forward gear stage, preferably formed as a direct gear, is provided by the engagement of the first, second and third clutches 13, 16, 67, and the seventh forward gear stage is made of the first gear. Provided by the engagement of the first, second and fourth clutches 13, 16 and 48, the eighth forward shift stage is provided by the engagement of the first, third and fourth clutches 13, 67 and 48 The ninth forward shift stage includes the second brake O4 and the first and It is provided by the engagement of the third clutches 13 and 67, and the reverse shift stage is provided by the engagement of the first brake O3 and the third and fourth clutches 67 and 48.

By engaging the first brake O3 and the fourth clutch 48 at the first forward gear stage and the first reverse gear stage, the shifting members can be used as starting members.

In the case where the fourth clutch 48 is omitted in accordance with the embodiment of FIG. 2, that is, the second planetary gear set made through the eighth shaft 8, the fourth clutch 48, and the fourth shaft 4 ( In the case where the detachable connection of the ring gear of P2 and the carrier of the first planetary gear set P1 is replaced by direct connection by the fourth shaft 4, the fourth clutch 48 in the shifting pattern is shown in FIG. 2. Is replaced by an additional clutch 18 removably connecting the input shaft 1 and the additional shaft 8 'which is connected to the sun gear of the first planetary gear set P1.

Further, according to the present invention, even when the transmission diagrams are the same, various adjacent transmission ratio differences are provided according to respective shifting logics, thereby enabling a variation specific to an application or a variation specific to a vehicle.

According to the invention further one-way clutches can be provided at each suitable position of the multi-stage transmission, for example between one shaft and the housing, or to connect two shafts as the case may be.

On the input side, or on the output side, an axle differential and / or inter-axis differential can be arranged according to the invention.

In the scope of the preferred refinement embodiment, the input shaft 1 can be separated from the drive engine as required by the clutch member, and the clutch member may be a hydrodynamic converter, a fluid clutch, or a dry starting clutch, a wet starting clutch, an electromagnetic clutch, Or a centrifugal clutch can be used. It is also possible to arrange this type of starting member behind the transmission in the direction of the power flow, in which case the input shaft 1 is continuously connected with the crankshaft of the engine.

In addition, the multi-stage transmission according to the present invention makes it possible to arrange a torsional vibration damper between the engine and the transmission.

In the category of further non-illustrated embodiments of the invention, wear-free brakes, such as hydraulic or electric retarders, on each shaft, preferably on the input shaft 1 or the output shaft 2, for example. free brakes can be arranged, which is particularly important for use in commercial vehicles. In addition, a power take-off can be provided on each shaft, preferably on the input shaft 1 or on the output shaft 2 for the driving of additional units.

The friction shifting members used may be formed as a power-shifting clutch or brake. In particular non-positive clutches or brakes can be used, such as, for example, multi-plate clutches, band brakes and / or cone clutches.

A further advantage of the multistage transmission introduced herein can be mounted on each shaft as an electric machine as a generator and / or an additional drive machine.

In addition, it is obvious that each structural shape, in particular the respective spatial arrangements of the planetary gear sets and the shifting members themselves and each other, is technically important, although the shape is explicitly illustrated. Even if not shown or described in the specification, it is within the protection scope of the claims of the present application without affecting the function of the transmission as specified in the claims.

0: shaft
1: first shaft, input shaft
2: second shaft, output shaft
3: third shaft
4: fourth shaft
5: fifth shaft
6: sixth shaft
7: 7th shaft
8: eighth shaft
8 ': additional shaft
O3: first brake
O4: second brake
13: first clutch
16: second clutch
18: additional clutch
48: fourth clutch
67: third clutch
P1: first planetary gear set
P2: 2nd planetary gear set
P3: 3rd planetary gear set
P4: fourth planetary gear set
i: speed ratio
phi: adjacent gear ratio difference
G: housing

Claims (5)

An input shaft 1, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4 arranged inside the housing G and a total of eight rotatable shafts 1, 2, 3 and 4 , 5, 6, 7, 8, 8 ′, as well as six or more shifting members O3, O4, having brakes O3, O4 and clutches 13, 16, 18, 48, 67. 13, 16, 18, 48, 67), a multi-speed transmission with a planetary gear structure, in particular an automatic transmission for automobiles,
In the multi-stage transmission, the selective engagement of the shifting members generates various speed ratios between the input shaft 1 and the output shaft 2 so that nine forward and one reverse gear stages can be realized. ,
The sun gear of the first planetary gear set P1 is operatively connected with the input shaft 1, which is connected to the third shaft 3 via the first clutch 13 and to the second clutch. The sixth shaft 6 may be detachably connected to the sixth shaft 6, and the third shaft 3 may be connected to the carrier of the second planetary gear set P2 and the ring gear of the third planetary gear set P3. Connected to the housing G of the transmission via the first brake O3, and the fourth shaft 4 may be coupled to the housing G of the transmission via the second brake O4, and 2 is connected to the ring gear of the planetary gear set P2 and operatively connected to the carrier of the first planetary gear set P1, and the sixth shaft 6 is connected to the sun gear of the fourth planetary gear set P4 and It can be detachably connected with the seventh shaft 7 via the three clutch 67, the seventh shaft is the sun gear and the second planetary gear set P of the third planetary gear set P3 Is connected to the sun gear of 2), the ring gear of the first planetary gear set P1 is rotatably connected to the housing G of the transmission, and the fifth shaft 5 is of the third planetary gear set P3. And a output gear (2) connected to a carrier and a ring gear of a fourth planetary gear set (P4), the output shaft (2) connected to a carrier of a fourth planetary gear set (P4). 2. The sun gear of claim 1, wherein the sun gear of the first planetary gear set P1 is directly connected to the input shaft 1, and the carrier of the first planetary gear set P1 is the first planetary gear set ( An eighth shaft 8 connected to the carrier of P1, a fourth clutch 48 detachably connecting the fourth shaft 4 and the eighth shaft 8 to each other, and the second planetary gear set Multi-speed transmission, characterized in that through the fourth shaft (4) connected to the ring gear of the second planetary gear set (P2) can be detachably connected. The sun gear according to claim 1, wherein the sun gear of the first planetary gear set P1 includes an additional shaft 8 'which is connected to the sun gear of the first planetary gear set P1, and the additional shaft 8'. And an additional clutch 18 detachably connecting the input shaft 1 with the input shaft 1, and the carrier of the first planetary gear set P1 is connected to the fourth. Multi-speed transmission, characterized in that directly connected to the ring gear of the second planetary gear set (P2) via a shaft (4). The multi-speed transmission as claimed in one of the preceding claims, characterized in that the planetary gear sets (P1, P2, P3, P4) are formed as a negative planetary gear set. 4. The first forward gear stage according to claim 2 or 3, wherein the sun gear of the first planetary gear set P1 is directly connected to the input shaft 1, wherein the first forward gear stage is formed of the first brake O3 and the first brake gear. By the engagement of the second and fourth clutches 16, 48, the second forward shift stage is engaged by the engagement of the first and second brakes O3, O4 and the second clutch 16. By engaging the first brake O3 and the second and third clutches 16 and 67, the fourth forward shift stage is connected to the engagement of the second brake O4 and the second and third clutches 16 and 67. Thereby, the fifth forward shift stage is engaged with the second, third and fourth clutches 16, 67, and 48, and the sixth forward shift stage has the first, second and third clutches 13, 16, and 67. ), The seventh forward shifting stage engages the first, second and fourth clutches 13, 16 and 48, and the eighth forward shifting stage engages the first, third and fourth clutches 13. , 67, 48, the ninth forward shift stage is connected to the second brake O4 and the first and third clutches 1. By the fastening of 3 and 67, the reverse shift stage is made by the fastening of the first brake O3 and the third and fourth clutches 67 and 48, and the line of the first planetary gear set P1. An additional shaft 8 ', in which a gear is connected to the sun gear of the first planetary gear set P1, and an additional clutch 18, which removably connects the additional shaft 8' and the input shaft 1; And the fourth clutch (48) is replaced by an additional clutch (18) if it can be detachably connected to the input shaft (1).

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